EP1001170A2 - Variable displacement compressor - Google Patents
Variable displacement compressor Download PDFInfo
- Publication number
- EP1001170A2 EP1001170A2 EP99119776A EP99119776A EP1001170A2 EP 1001170 A2 EP1001170 A2 EP 1001170A2 EP 99119776 A EP99119776 A EP 99119776A EP 99119776 A EP99119776 A EP 99119776A EP 1001170 A2 EP1001170 A2 EP 1001170A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- refrigerant
- low
- main valve
- chamber
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1809—Controlled pressure
- F04B2027/1813—Crankcase pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1822—Valve-controlled fluid connection
- F04B2027/1827—Valve-controlled fluid connection between crankcase and discharge chamber
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/184—Valve controlling parameter
- F04B2027/1859—Suction pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B27/00—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders
- F04B27/08—Multi-cylinder pumps specially adapted for elastic fluids and characterised by number or arrangement of cylinders having cylinders coaxial with, or parallel or inclined to, main shaft axis
- F04B27/14—Control
- F04B27/16—Control of pumps with stationary cylinders
- F04B27/18—Control of pumps with stationary cylinders by varying the relative positions of a swash plate and a cylinder block
- F04B27/1804—Controlled by crankcase pressure
- F04B2027/1863—Controlled by crankcase pressure with an auxiliary valve, controlled by
- F04B2027/1881—Suction pressure
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
- The present invention relates to a variable displacement compressor used for compressing refrigerant in a refrigeration cycle of an automobile air conditioner or the like, comprising an airtight crank chamber and a variable inclination angle swing body installed on an axis of rotation inside said crank chamber, comprising at least one piston reciprocally guided in a cylinder and connected to said swing body, said cylinder being selectively connectable to a suction chamber in turn connected to a low-pressure refrigerant pipe conduit or to a discharge chamber in turn connected to a low-pressure refrigerant pipe conduit, and means in said variable displacement compressor for varying the amount of discharge of said refrigerant into said discharge chamber between a minimum discharge amount in a minimum operation state of the compressor and a maximum discharge amount by varying the angle of inclination of said swing body corresponding to a change of a pressure within said crank chamber, and further comprising a main valve between said low-pressure refrigerant pipe conduit and said suction chamber, said main valve being actuable between a fully closed state and a fully opened state.
- As the compressor used in a refrigeration cycle of an automobile air conditioner has a belt directly connected to the engine by a transmission belt, the number of its rotations cannot be controlled independently from engine speed. So a variable displacement compressor is used which can change the amount of refrigerant (the amount of discharge) to obtain the appropriate cooling capacity without being restricted by the number of rotations of the engine. In such a variable displacement compressor, a swing plate is generally installed in an airtight crank chamber so as to be able to tilt over a variable angle of inclination. The swing plate is driven by rotational movement of the axis of rotation and executes swing movements. A piston executing reciprocal motions by the swing movements of the swing plate sucks refrigerant of a suction chamber connected to a low-pressure refrigerant pipe conduit into a cylinder, compresses it, and discharges it to a discharge chamber connected to a high-pressure refrigerant pipe conduit. The amount of discharge of the refrigerant is changed by changing the angle of inclination of the swing plate according to change of pressure of the crank chamber. The variable displacement compressor used for a refrigeration cycle of an automobile air conditioner generally continues to operate even when cooling capacity is not needed, with a minimum displacement which is about 5% of the maximum displacement. That is, the compressor then operates at the minimum operation state. However, if simply operated like that, the problem occurs that even at the minimum operation state fins of the evaporator freeze when the load is small as in winter, due to a flow of compressed refrigerant into the evaporator So, a valve is installed to enable a passage between the low-pressure refrigerant pipe conduit and the suction chamber to be fully closed, thereby preventing the low-pressure refrigerant from being sucked into the compressor at the minimum operation state. The conventional variable displacement compressor used in a refrigeration cycle of an automobile air conditioner makes the passage between the low-pressure refrigerant pipe conduit and the suction chamber to be fully closed at the minimum operation, irrespective of the season. However, freezing of the fins of the evaporator is a problem which occurs only when the load is small, as in winter. The problem of freezing does not occur, when the load is higher, as in summer. The load of the compressor for the engine produced by having closed the inlet of the compressor leads to a disadvantageous result because fuel efficiency decreases.
- Therefore, the present invention aims to provide a variable displacement compressor with improved fuel efficiency which does not generate freezing of the fins of the evaporator at the minimum operation state, when the load is small, as in winter, and which reduces the load to the engine when the load is large, as in summer.
- Said task can be achieved with a variable displacement compressor according to
claim 1,claim 2,claim 3 orclaim 4. - According to a first aspect of the invention a main valve actuating structure is provided, actuating the main valve by refrigerant pressure into its closed state, said main valve actuating means being responsive to a relative pressure condition or a relative temperature condition of the refrigerant in the low-pressure pipe conduit, said relative pressure condition or relative temperature condition representing during said minimum operation state of said compressor a small load condition.
- Since said main valve actuating structure is responsive to a relative pressure condition or a relative temperature condition of the refrigerant in the low-pressure pipe conduit which condition is representing either a small load condition and simultaneously said minimum operation state of the compressor or a large load condition, the main valve automatically is brought into a fully closed state only in case of a small load condition and simultaneously with a minimum operation state of the compressor. This means that in case of higher load conditions as in summer and during a minimum operation state of the compressor with the not fully closed main valve the power consumption of the compressor is low, improving the fuel efficiency of the engine driving the compressor. This is based on the recognition that in a large load condition as in summer there is no danger of fin freezing even though the compressor supplies a small amount of refrigerant to the evaporator. Operation of the compressor with fully closed main valve occurs only in case of a small load condition during the minimum operation state of the compressor and to the benefit of the elimination of the danger of fin freezing, e.g. as in winter with low ambient temperature.
- According to a further aspect of the invention as said main valve a differential-pressure sensing open and close valve is provided which opens and closes respectively when a differential pressure Pd minus Pe between the pressure Pd of the refrigerant in said discharge chamber and the pressure of the refrigerant in said low-pressure refrigerant pipe conduit is larger or smaller than a predetermined differential pressure value.
- According to a further aspect of the invention as a main valve a temperature sensing open and close valve for low-pressure refrigerant is provided between said low-pressure refrigerant pipe conduit and said suction chamber which opens and closes respectively when the temperature of the refrigerant in said suction chamber and/or in said low-pressure pipe conduit is higher or lower than a predetermined temperature value.
- According to a further aspect of the invention as a main valve a pressure sensing open and close valve for low-pressure refrigerant is provided between the low-pressure refrigerant pipe conduit and said suction chamber which opens and closes respectively when the pressure of the refrigerant in said low-pressure refrigerant pipe conduit is lower or higher than a predetermined pressure value.
- The present invention enables the inlet of a variable displacement compressor used in a refrigeration cycle of an automobile air conditioner automatically to be closed when the load is small and opened when the load is large. So, freezing of fins of an evaporator can be avoided at the minimum operation state with a small load for the engine, as in winter, and the fuel efficiency can be improved by reducing the load for the engine when the load is large, as in summer.
- A refrigerant reflux conduit connecting the discharge chamber and the low-pressure refrigerant pipe conduit with a small cross-sectional area and only when the main valve is closed allows by a backflow of refrigerant to keep the pressure in the low-pressure refrigerant pipe conduit on a level which is not too much below the predetermined pressure value as long as the main valve is closed.
- When the closure member of the main valve is connected to an actuating piston member provided in a driving chamber communicating via a drive line with said discharge chamber, the pressure of the refrigerant in the system can be used to actuate the main valve accordingly. The pressure in the discharge chamber has the function of a pilot pressure mainly for adjusting and maintaining the main valve closed position.
- In order to avoid undesirable pressure forces on the main valve displacement structure said structure ought to be pressure balanced either with respect to the pressure in the low-pressure pipe conduit or to the pressure in the suction chamber.
- If the differential pressure used to actuate the main valve is derived from the pressure in the discharge chamber and the pressure in the low-pressure pipe conduit said differential pressure ought to be active in parallel to the force of a main valve closing spring which determines the differential pressure value at which the main valve will be closed.
- If, alternatively, the relative differential pressure used to actuate the main valve is derived from the discharge chamber pressure and the suction chamber pressure, said differential pressure ought to be active in closing direction of the main valve and counter to the force of a weak valve opening spring.
- In order to allow a backflow of refrigerant from said driving chamber into said low-pressure pipe conduit to control the pressure in the low-pressure pipe conduit accordingly, a valve structure in said reflux conduit exclusively opens when the main valve is closed. This easily can be controlled in strict dependence from the stroke position of said piston member actuating the closure member of the main valve. By said measure a backflow of refrigerant is blocked whenever the main valve is in an open state.
- In case that the valve structure in the drive line is connected to a temperature responsive drive member contacted by the refrigerant in the low-pressure pipe conduit the temperature of the refrigerant can be sensed reliably in order to shift the main valve into the closed state in case that the temperature value represents a small load condition and simultaneously a minimum operation state of the compressor.
- For that purpose a flexible bimetallic drive member which optionally is spring-loaded in both flexing directions to perform a bi-stable performance is advantageous.
- Alternatively the valve structure contained in the drive line can be connected to a pressure responsive drive member responding to the pressure of the refrigerant in the low-pressure pipe conduit in order to bring said valve structure into an open state and to reliably close the main valve, in case that the pressure of the refrigerant is representing a small load condition and simultaneously the minimum operation state of the compressor.
- For this purpose a diaphragm is of advantage which is contacted by the refrigerant in closing direction of said valve structure and is loaded on the opposite side by a reference pressure like the atmospheric pressure.
- It is advantageous to have a bleeding channel connecting the suction chamber and said driving chamber and a flow restrictor within said bleeding channel allowing a restricted communication for the refrigerant.
- If the reflux conduit is connecting said driving chamber and said low-pressure pipe conduit, said reflux conduit ought to be blocked in the open state of the main valve and only ought to be open in the closed state of the main valve in order to control the pressure in the low-pressure pipe conduit.
- In any case the main valve in its closed state could allow a flow of refrigerant towards the suction chamber just sufficient to provide the necessary lubrication for the compressor by this leaking refrigerant amount. However, said leaking amount ought to be limited such that in case of low load fin freezing of the evaporator is suppressed reliably.
- Embodiments of the invention will be described with the help of the drawing. In the drawing is:
- Figs 1 and 4
- Sectional views of a first embodiment of a valve structure at the suction side of a variable displacement compressor, in an open state and in a closed state, respectively,
- Figs 2 and 3
- A schematic block diagram of a variable displacement compressor containing the valve structure of Figs 1 and 4, illustrating the compressor in the maximum displacement state or the maximum operation state, and the minimum displacement state or minimum operation state, respectively,
- Figs 5 and 6
- Sectional views of another embodiment of a valve structure for the variable displacement compressor, in an opened state and a fully closed state, respectively,
- Figs 7 and 8
- Sectional views of a further embodiment of the valve structure for the variable displacement compressor, in a fully opened state and in a fully closed state, respectively,
- Figs 9 and 10
- Sectional views of a further embodiment of a valve structure for the variable displacement compressor, in a fully opened and in a fully closed state, respectively,
- Figs 11 and 12
- Sectional views of a further embodiment of a valve structure for the variable displacement compressor, in a fully opened and in a fully closed state, respectively,
- Figs 13 and 14
- Sectional views of a further embodiment of a valve structure for the variable displacement compressor, in a fully opened and in a fully closed state, respectively,
- Figs 15 and 16
- Sectional views of a further embodiment of a valve structure for the variable displacement compressor, in a fully opened and in a fully closed state, respectively, and
- Fig. 17
- A sectional view of a further embodiment of a valve structure for the variable displacement compressor, in a fully opened and pressureless state.
- In Figs 2 and 3 a
variable displacement compressor 10 is shown used in a refrigeration cycle of an automobile air conditioner Thecompressor 10 includes anairtight crank chamber 12 containing anaxis 11 of rotation driven by adriving pulley 13. Aswing plate 14 withincrank chamber 12 is tilted with respect to theaxis 11 of rotation and swings in accordance with a rotation of the axis ofrotation 11. Acylinder 15 provided e.g. incrank chamber 12 receives areciprocal piston 17 in a peripheral part of thecrank chamber 12. Arod 18 connectspistons 17 andswing plate 14 with another. When theswing plate 14 swings, thepiston 17 executes reciprocal motions in thecylinder 15. Via, not shown, conventional valve means asuction chamber 3 and adischarge chamber 4 are connected tocylinder 15. Refrigerant is drawn into thecylinder 15 fromsuction chamber 3 arranged at the upstream side ofcylinder 15, then is compressed incylinder 15, and thereafter is discharged to dischargechamber 4 located at a downstream side. - Low-pressure refrigerant is supplied to
suction chamber 3 from a low-pressurerefrigerant pipe conduit 1 located upstream ofsuction chamber 3. High-pressure refrigerant is discharged fromdischarge chamber 4 to a high-pressurerefrigerant pipe conduit 2 located downstream thereof. Pe is the pressure in the low-pressurerefrigerant pipe conduit 1; Ps is the pressure in thesuction chamber 3; Pd is the pressure of the refrigerant in thedischarge chamber 4; and Pc is the pressure inside thecrank chamber 12. - The angle of inclination of the
swing plate 14 in relation to theaxis 11 of rotation changes according to the pressure Pc. The amount of discharge of refrigerant fromcylinder 15, i.e. the capacity of thecompressor 10, changes by the angle of inclination of theswing plate 14. If a condition Pc equals Ps occurs, the state of the maximum displacement shown in Fig. 2 is achieved. If Pc is increasing, finally the state of the minimum displacement or the minimum operation state of thecompressor 10 as shown in Fig. 3 is achieved. - A
displacement control apparatus 5 controls displacement of thecompressor 10 by automatically controlling the crank chamber pressure Pc in correspondence to a change of the suction chamber pressure Ps.Displacement control apparatus 5 changes its control level electromagnetically. - A main valve 20 (Figs 1 to 4) is provided at the suction side of the compressor and is designed as a differential-pressure sensing open and close valve which opens and closes a passage between low-pressure
refrigerant pipe conduit 1 andsuction chamber 3 by means of avalve seat 22 and avalve closure member 21. Saidmain valve 20 is designed so that it does not close when the load is large as in summer and does close automatically only when the load is small as in winter, and when the variable displacement compressor is in its minimum operation state (Fig. 3). - In Figs. 1 and 4 said
main valve 20 is designed as a differential-pressure sensing open and close valve according to a first embodiment. Fig. 1 is illustrating an open state when the load is large as in summer, while Fig. 4 is illustrating a closed state when the load is small as in winter. -
Closure member 21 is provided opposing tovalve seat 22 from the upstream side thereof.Valve seat 22 is arranged between low-pressurerefrigerant pipe conduit 1 andsuction chamber 3. Apiston body 23 is integrally connected toclosure member 21 by a connectingrod 25.Piston body 23 is provided in a driving chamber where pressure Pd of thedischarge chamber 4 acts on the space at the rear side ofpiston body 23 via a driving high-pressure-side pipe 24. - The pressure receiving area of
piston body 23 and the sectional area ofvalve seat 22 are essentially equal. For that reason the suction chamber pressure Ps betweenclosure member 21 andpiston body 23 is cancelled, i.e. is balanced, so that it does not create any displacement force on the actuating structure constituted byclosure member 21 andpiston body 23. A differential pressure (Pd minus Pe) between pressure Pd in thedischarge chamber 4 and the pressure Pe in the low-pressurerefrigerant pipe conduit 1 acts on the actuating structure formed byclosure member 21 andpiston body 23. Acompression coil spring 26 defining a main valve closing spring acts onclosure member 21 at the upstream side thereof.Compression coil spring 26 is seated at afixed spring support 27 at the side of low-pressurerefrigerant pipe conduit 1. - As a result,
closure member 21 is lifted fromvalve seat 22 and falls into a valve open state (Fig. 1) when the value of the differential pressure (Pd minus Pe) between the pressure Pd of thedischarge chamber 4 and the pressure Pe of the low-pressurerefrigerant pipe conduit 1 becomes larger than the force ofcompression coil spring 26, such that the force ofcompression coil spring 26 determines the differential pressure value for opening and closing said main valve. - To the contrary, when the value of differential pressure Pd minus Pe is smaller than the force of
compression coil spring 26closure member 21 is pushed ontovalve seat 22 and falls into a valve closed state (Fig. 4). - However, even in the valve-closed state a minimum amount of refrigerant should be allowed to pass through the main valve in order to cool and lubricate the
variable displacement compressor 10, e.g. the closure function constituted betweenclosure member 21 andvalve seat 22 is intentionally formed so as to be imperfect. As an alternative, a leak hole may be provided inclosure member 21 or acrossvalve seat 22. Said measure allowing a minimum amount of refrigerant to pass through the closed main valve can be similarly applied to each following embodiment of the inventive valve structure. - If the value of the differential pressure Pd minus Pe with which the
main valve main valve refrigerant pipe conduit 1 and thesuction chamber 3 is closed when the load is small, e.g. as in winter, and is open when the load is large, e.g. as in summer. - If the load is small, no refrigerant is sucked into the
variable displacement compressor 10 from the low-pressure conduit pipe 1. So freezing of the fins of the evaporator (not shown) can be avoided even when the compressor continues to operate at the minimum operation state. If, on the other hand, the load is large, an amount of refrigerant corresponding to the operation state is sucked into thevariable displacement compressor 10 from the low-pressure conduit pipe 1 even at the minimum operation state of thecompressor 10. As a consequence, superfluous load is not applied by thecompressor 10 to the engine (not shown) driving the compressor and the fuel efficiency of the engine can be improved. - The structure of the embodiment of the
main valve 20 of Figs 5 and 6 additionally is equipped with arefrigerant reflux conduit 28, e.g. at the position of the axis of connectingrod 25. Saidconduit 28 allows to connect the driving chamber at the rear side ofpiston body 23 to be connected to the low-pressurerefrigerant pipe conduit 1. Arefrigerant reflux valve 29 is provided which closes the inlet ofconduit 28 in case thatmain valve Valve 22 includes a rod loosely fitted into conduit 28 (a longitudinal channel in the interior of connecting rod 25) and a valve member seated in the top mouth ofconduit 28.Spring support 27 is formed with a recess receiving the valve member and a weak valve closure spring in the open state ofmain valve 21, 22 (Fig. 5). Therod 25 can have a longitudinal extension such that it abuts on the bottom of drive chamber ofpiston body 23 whenclosure member 21 is seated onvalve seat 22 in order to open refrigerant reflux valve 29 (Fig. 6). The flow of refrigerant throughreflux conduit 28 is restricted whenvalve 29 is its open position (Fig. 6). - Via
refrigerant reflux conduit 28 the pressure Pd in thedischarge chamber 4 is transmitted to the low-pressurerefrigerant pipe conduit 1 so that pressure Pe in the low-pressure pipe conduit 1 can be controlled so as not to be too much below a predetermined pressure value. However, not only the pressure is transmitted but also a reflux of a lubricant or lubricating refrigerant is executed. - In the embodiment of Figs 7 and 8 the
valve structure 20 includes therefrigerant reflux conduit 28 separately provided without using the connectingrod 25,Conduit 28 instead extends fromdischarge chamber 4 laterally into the driving chamber ofpiston body 23 and continues laterally from said driving chamber to low-pressure pipe conduit 1.Piston body 23 functions as a control piston slide for either opening or closingconduit 28, depending on the stroke position ofpiston body 23.Conduit 28 exclusively is open whenpiston body 23 is in a stroke position corresponding to the fully closed state ofmain valve - In the embodiment of Figs 9 and 10 of the
valve structure 20 therefrigerant reflux conduit 28 is provided inside connectingrod 25. Similar as in Figs 7 and 8piston body 23 has the function of a control pistonslide opening conduit 28 exclusively in a stroke position corresponding to the closed state ofmain valve main valve piston body 28 is blockingconduit 28. - In the embodiment of the
valve structure 120 if Figs 11 and 12 a temperature sensing open and close valve is used as the main valve for low-pressure refrigerant. Invalve structure 120closure member 21 structurally is connected topiston body 23 by connectingrod 25.Closure member 21 biased by aweak compression spring 126 constituting a main valve opening spring. Pressure Pd in thedischarge chamber 4 acts via driving high-pressure side pipe 24 on the rear side ofpiston body 23 situated in its driving chamber. In this embodiment, however, the pressure Ps in thesuction chamber 3 is acting onclosure member 21 in opening direction ofmain valve refrigerant pipe conduit 1 is cancelled or is balanced for bothclosure member 21 andpiston body 23. The spring force of compression coil spring 126 (main valve opening spring) is very weak compared with the force ofcompression coil spring 26 of the preceding embodiments.Compression coil spring 126 does not have force enough to overcome the differential pressure (Pd minus Ps). - In the extension of the driving pipe 24 a high-pressure pipe open and
close valve 32 is installed which is connected to a temperature responsive driving member, e.g. abimetallic member 31, sensing the temperature of the refrigerant in the low-pressurerefrigerant pipe conduit 1.Bimetallic member 31 is pre-loaded by springs in both direction of its flexing displacement. Moreover, a cross channel (shown in dotted lines) connectssuction chamber 3 and driving chamber ofpiston body 23. Said channel contains a leak hole or aflow restrictor 34 having a sectional area which is smaller than that of the drivingpipe 24, in order to e.g. relieve the pressure at the back side of thepiston body 23 whenmain valve - When the temperature of the refrigerant in the low-pressure
refrigerant pipe conduit 1 is higher than, e.g., 0°C (when the load is large), thebimetallic member 31 drivesvalve structure 32 into a closed state (Fig. 11). As a result, the pressure in the driving chamber or at the rear side ofpiston body 23 becomes the same as pressure Ps insuction chamber 3 due to the equalising influence of the channel with itsleak hole 34. Since then the actuating structure consisting ofclosure member 21 andpiston body 23 is pressure balanced the pressure of the refrigerant does not act onmain valve Closure member 21 is brought into its open position bycompression coil spring 126 so that low-pressurerefrigerant pipe conduit 1 andsuction chamber 3 fall into a mutually connected state. - When the temperature of the refrigerant in the low-pressure
refrigerant pipe conduit 1 is lower than, e.g. 0°C (when the load is small), thebimetallic member 31 drives thevalve structure 32 into its open state (Fig. 12). - As a result, the pressure at the rear side of the
piston body 23 is the same as pressure Pe indischarge chamber 4. Then differential pressure Pd minus Ps derived from the pressures in thedischarge chamber 4 and thesuction chamber 3 is acting on the actuation structure consisting ofclosure member 25 andpiston body 23 such thatclosure member 21 is pressed againstvalve seat 22 into the closed state ofmain valve refrigerant pipe conduit 1 and thesuction chamber 3 falls into a closed state. The already mentioned minimum amount of refrigerant still passes through themain valve - In the embodiment of Figs 13 and 14 the
refrigerant reflux conduit 28 connects the rear side of thepiston body 23 in driving chamber to the low-pressurerefrigerant pipe conduit 1. Opening and closing ofconduit 28 is controlled by movement ofpiston body 23 such thatconduit 28 is only open when themain valve refrigerant pipe conduit 1 is connected to the drivingpipe 24 viaconduit 28 at the same time such that pressure from thedischarge chamber 4 is returned to the low-pressurerefrigerant pipe conduit 1, e.g., in order to control the pressure inconduit 1. - In the embodiment of Figs 15 and 16 a temperature sensing open and
close valve structure 120 in therefrigerant reflux conduit 28 is formed in a different way. The rear end section ofpiston body 23 is formed with a cut-out or shoulder co-operating with the inner wall of the driving chamber forpiston body 23 such that only in a predetermined stroke position ofpiston body 23conduit 28 will be open (in the close state of themain valve 21, 22). As soon as the shoulder or recess ofpiston body 23 is entering into the drivingchamber conduit 28 will be cut off.Closure member 21 in this embodiment slidably is carried by connectingrod 25.Compression coil spring 126 is acting onclosure member 21 in opening direction ofmain valve supplementary spring 35 is loadingclosure member 21 in the opposite direction towards a stop provided on connectingrod 25. In case of small load, that is the closed state ofmain valve 21, 22 (Fig. 16),closure member 21 abuts againstvalve seat 22. Thereafterpiston body 23 is moved further by the pressure in its driving chamber untilrefrigerant reflux conduit 28 is opened and low-pressurerefrigerant pipe conduit 1 is connected to drivingpipe 24. - In the embodiment of Fig. 17
main valve close valve 220 for low-pressure refrigerant. Avalve structure 36 includingvalve 32 is provided in drivingpipe 24 or at its inlet region indischarge chamber 4. Saidvalve structure 36 is connected with a pressure responsive driving member like adiaphragm 361 hermetically sealing a chamber connected to low-pressure pipe conduit 1 from atmospheric pressure or a reference pressure.Diaphragm 361 senses the pressure in the low-pressure conduit pipe 1 in closing direction ofvalve structure 36 and is effected by the atmospheric pressure in the opposite direction. Compression springs, acting on both sides ofdiaphragm 361 maintain thediaphragm 361 in a predetermined position and determine the pressure value at which diaphragm 361 starts to bringvalve structure 36 into its closed state. A corresponding setting or adjustment of thevalve structure 36 allows to open themain valve refrigerant pipe conduit 1. As long as in a condition of large load the pressure Pe in low-pressure conduit pipe 1 is relatively high,diaphragm 361 holdsvalve structure 36 in its closed state. Drivingpipe 24 is blocked. Viarestrictor 34 the pressure in the driving chamber of thepiston body 23 corresponds to Ps. The weak force ofspring 126 adjustsmain valve pressure Pe diaphragm 361 is opening valve structure 36 (as shown). Drivingline 24 is then connected to dischargechamber 4 so thatpiston body 23 will be displaced to the left closingmain valve - The expression "small load or when the load is low as in winter time" means that the "cooling demand" for the refrigerant cycle is reduced due to low ambient temperature in this season. This further means that the "thermal Load" for the air conditioning system also will be reduced.
Claims (16)
- A variable displacement compressor (10), comprising an airtight crank chamber (12) and a variable inclination angle swing body (14) installed on an axis (11) of rotation inside said crank chamber (12), at least one piston (17) reciprocally guided in a cylinder (15) and connected to said swing body, said cylinder (15) being selectively connectable to a suction chamber (3) in turn connected to a low-pressure refrigerant pipe conduit (1) or to a discharge chamber (4) in turn connected to a high-pressure refrigerant pipe conduit (2), and means in said variable displacement compressor (10) for varying the amount of discharge of said refrigerant into said discharge chamber (4) between a minimum discharge amount in a minimum operation state of the compressor and a maximum discharge amount by varying the angle of inclination of said swing body corresponding to a change of a pressure (Pc) within said crank chamber, and further comprising a main valve (21, 22) between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3), said main valve being actuable between a fully closed state and a fully opened state, wherein a main valve actuating structure (23, 24, 32, 36) is provided actuating said main valve by refrigerant pressure into its closed state, said main valve actuating structure being responsive to a relative pressure condition or a relative temperature condition of the refrigerant in the low-pressure pipe conduit (1), which relative pressure condition or relative temperature condition in said minimum operation state of said compressor (10) is representing a small load condition.
- A variable displacement compressor (10), comprising an airtight crank chamber (12) and a variable inclination angle swing body (14) installed on an axis (11) of rotation inside said crank chamber (12), at least one piston (17) reciprocally guided in a cylinder (15) and connected to said swing body, said cylinder (15) being selectively connectable to a suction chamber (3) in turn connected to a low-pressure refrigerant pipe conduit (1) or to a discharge chamber (4) in turn connected to a high-pressure refrigerant pipe conduit (2), and means in said variable displacement compressor (10) for varying the amount of discharge of said refrigerant into said discharge chamber (4) between a minimum discharge amount in a minimum operation state of the compressor and a maximum discharge amount by varying the angle of inclination of said swing body corresponding to a change of a pressure (Pc) within said crank chamber, and further comprising a main valve (21, 22) between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3), said main valve being actuable between a fully closed state and a fully opened state, wherein as said main valve a differential-pressure sensing open and close valve (21, 22, 23, 24) is provided which opens and closes respectively when a differential pressure (Pd) minus (Pe) between the pressure (Pd) of the refrigerant in said discharge chamber (4) and the pressure of the refrigerant in said low-pressure refrigerant pipe conduit (1) is larger or smaller than a predetermined differential pressure value.
- A variable displacement compressor (10), comprising an airtight crank chamber (12) and a variable inclination angle swing body (14) installed on an axis (11) of rotation inside said crank chamber (12), at least one piston (17) reciprocally guided in a cylinder (15) and connected to said swing body, said cylinder (15) being selectively connectable to a suction chamber (3) in turn connected to a low-pressure refrigerant pipe conduit (1) or to a discharge chamber (4) in turn connected to a high-pressure refrigerant pipe conduit (2), and means in said variable displacement compressor (10) for varying the amount of discharge of said refrigerant into said discharge chamber (4) between a minimum discharge amount in a minimum operation state of the compressor and a maximum discharge amount by varying the angle of inclination of said swing body corresponding to a change of a pressure (Pc) within said crank chamber, and further comprising a main valve (21, 22) between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3), said main valve being actuable between a fully closed state and a fully opened state, wherein as said main valve a temperature sensing open and close valve (21, 22, 23, 24, 32) for low-pressure refrigerant is provided between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3) which opens and closes respectively when the temperature of the refrigerant in said suction chamber (3) and/or said low-pressure pipe conduit (1) is higher or lower than a predetermined temperature value.
- A variable displacement compressor (10), comprising an airtight crank chamber (12) and a variable inclination angle swing body (14) installed on an axis (11) of rotation inside said crank chamber (12), at least one piston (17) reciprocally guided in a cylinder (15) and connected to said swing body, said cylinder (15) being selectively connectable to a suction chamber (3) in turn connected to a low-pressure refrigerant pipe conduit (1) or to a discharge chamber (4) in turn connected to a high-pressure refrigerant pipe conduit (2), and means in said variable displacement compressor (10) for varying the amount of discharge of said refrigerant into said discharge chamber (4) between a minimum discharge amount in a minimum operation state of the compressor and a maximum discharge amount by varying the angle of inclination of said swing body corresponding to a change of a pressure (Pc) within said crank chamber, and further comprising a main valve (21, 22) between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3), said main valve being actuable between a fully closed state and a fully opened state, wherein as said main valve a pressure sensing open and close valve (21, 22, 23, 24, 36) for low-pressure refrigerant is provided between said low-pressure refrigerant pipe conduit (1) and said suction chamber (3) which opens and closes respectively when the pressure of the refrigerant in said low-pressure refrigerant pipe conduit (1) is lower or higher than a predetermined pressure value.
- A variable displacement compressor as in claims 1, 2, 3 or 4, wherein a refrigerant reflux conduit (28) connects said discharge chamber (4) and said low-pressure refrigerant pipe conduit (1) exclusively when said main valve (21, 22) is separating said low-pressure refrigerant pipe conduit (1) and said suction chamber (3), said refrigerant reflux conduit having a small cross-sectional area.
- A variable displacement compressor as in claim 1, wherein the main valve (21, 22) comprises a valve seat (22) situated between said suction chamber (3) and said low-pressure conduit pipe (1), a closure member (21) arranged at the side of said valve seat (22) facing the low-pressure pipe conduit (1), and an actuating piston member (23) connected to said closure member (21) and situated in a driving chamber communicating via a driving line (24) with said discharge chamber (4), said closure member (21) and said actuating piston member (23) constituting said main valve displacement structure.
- A variable displacement compressor as in claim 6, wherein said main valve displacement structure is pressure balanced with respect either to said pressure (Pe) or to said pressure (Ps).
- A variable displacement compressor as in claim 1, wherein the relative pressure condition is a differential pressure (Pd) minus (Pe) derived from the pressure (Pd) within said discharge chamber (4) and the pressure (Pe) within said low-pressure conduit pipe (1), said differential pressure actuating said main valve (21, 22, 23, 24) in closing direction and in parallel to the force of a main valve closing spring (26).
- A variable displacement compressor as in claim 1, wherein the relative pressure condition is a differential pressure (Pd) minus (Ps) derived from the pressure (Pd) in said discharge chamber (4) and said pressure (Ps) in said suction chamber (3), said differential pressure actuating said main valve (21, 22) in closing direction and counter to the force of a main valve opening spring (126).
- A variable displacement compressor as in claim 6, wherein a refrigerant reflux conduit (28) connects said driving chamber and said low-pressure pipe conduit (1), and wherein a valve structure (29, 30) is provided in said refrigerant reflux conduit (28), said valve structure being in an open state in a stroke position of said piston member (23) corresponding to the closed state of said main valve (21, 22).
- A variable displacement compressor as in claim 6, wherein said driving line (24) receives a valve structure (32) connected to a temperature responsive drive member (31), said temperature responsive drive member (31) being contacted by the refrigerant in said low-pressure pipe conduit (1) to maintain said valve structure in an open state when the temperature of the refrigerant in the low-pressure pipe conduit (1) remains below a temperature value representing a small load condition and to maintain it in a closed state when the temperature of the refrigerant in the low-pressure pipe conduit (1) remains above a temperature value representing a large load condition.
- A variable displacement compressor as in claim 11, wherein said temperature responsive drive member (31) is a flexible bimetallic drive member which is spring loaded in both flexing directions.
- A variable displacement compressor as in claim 6, wherein said driving line (24) receives a valve structure (36) connected to a pressure responsive drive member (361), said pressure responsive drive member being situated in the refrigerant in said low-pressure pipe conduit (1) to maintain said valve structure (36, 32) in an open state when the pressure of the refrigerant in said low-pressure pipe conduit (1) remains below a pressure value representing a small load condition and to maintain it in a closed state when the pressure in said refrigerant in the low-pressure pipe conduit (1) represents a large load condition.
- A variable displacement compressor as in claim 13, wherein said pressure responsive drive member is a diaphragm one side of which is contacted in closing direction of said valve structure (36) by the refrigerant pressure (Pe) in low-pressure pipe conduit (1), the other side of which is contacted by a reference pressure like the atmospheric pressure.
- A variable displacement compressor as in claim 9, wherein a bleeding channel connects said suction chamber (3) and said driving chamber, said bleeding channel containing a flow restrictor (34) of smaller cross-sectional area than the cross-sectional area of said driving line (24).
- A variable displacement compressor as in claim 9, wherein a refrigerant reflux conduit (28) connects said driving chamber and said low-pressure pipe conduit (1), and wherein said reflux conduit (28) is blocked in the open state of the main valve (21, 22) and is open in the closed state of said main valve.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP32039198 | 1998-11-11 | ||
JP10320391A JP2000145629A (en) | 1998-11-11 | 1998-11-11 | Variable displacement compressor |
Publications (2)
Publication Number | Publication Date |
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EP1001170A2 true EP1001170A2 (en) | 2000-05-17 |
EP1001170A3 EP1001170A3 (en) | 2001-01-24 |
Family
ID=18120955
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99119776A Withdrawn EP1001170A3 (en) | 1998-11-11 | 1999-10-06 | Variable displacement compressor |
Country Status (3)
Country | Link |
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US (1) | US6267562B1 (en) |
EP (1) | EP1001170A3 (en) |
JP (1) | JP2000145629A (en) |
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EP1520987A1 (en) * | 2003-09-30 | 2005-04-06 | Fujikoki Corporation | Valve |
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EP2136080A1 (en) * | 2008-06-17 | 2009-12-23 | Delphi Technologies, Inc. | Variable displacement compressor with a discharge pressure compensated suction shutoff valve |
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EP1167899A3 (en) * | 2000-06-21 | 2002-03-20 | TGK Co., Ltd. | Supercooling degree control type expansion valve |
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CN103529150A (en) * | 2013-10-28 | 2014-01-22 | 徐继承 | Constant temperature gasification device-containing sample injection evaporator used for low pressure liquefied gas examination |
CN103543227A (en) * | 2013-10-28 | 2014-01-29 | 徐继承 | Sampling evaporator comprising automatic replacement device and used for low-pressure liquefied gas inspection |
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Also Published As
Publication number | Publication date |
---|---|
US6267562B1 (en) | 2001-07-31 |
EP1001170A3 (en) | 2001-01-24 |
JP2000145629A (en) | 2000-05-26 |
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